WO2016143230A1 - Dispositif d'étanchéité pour turbine à gaz, turbine à gaz et moteur d'aéronef - Google Patents

Dispositif d'étanchéité pour turbine à gaz, turbine à gaz et moteur d'aéronef Download PDF

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Publication number
WO2016143230A1
WO2016143230A1 PCT/JP2015/085882 JP2015085882W WO2016143230A1 WO 2016143230 A1 WO2016143230 A1 WO 2016143230A1 JP 2015085882 W JP2015085882 W JP 2015085882W WO 2016143230 A1 WO2016143230 A1 WO 2016143230A1
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WO
WIPO (PCT)
Prior art keywords
seal
turbine
gas turbine
closed space
seal portion
Prior art date
Application number
PCT/JP2015/085882
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English (en)
Japanese (ja)
Inventor
池田　和史
仁志 北川
勝人 荒木
能幸 岡部
Original Assignee
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to JP2017504581A priority Critical patent/JP6383088B2/ja
Priority to US15/554,572 priority patent/US10641118B2/en
Priority to DE112015006259.9T priority patent/DE112015006259T5/de
Priority to CN201580077457.5A priority patent/CN107407158B/zh
Publication of WO2016143230A1 publication Critical patent/WO2016143230A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/04—Antivibration arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/064—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces the packing combining the sealing function with other functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/54—Other sealings for rotating shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/32—Application in turbines in gas turbines
    • F05D2220/323—Application in turbines in gas turbines for aircraft propulsion, e.g. jet engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/35—Combustors or associated equipment

Definitions

  • the present invention provides, for example, a gas turbine in which compressed high-temperature and high-pressure air is supplied with fuel and burned, and the generated combustion gas is supplied to a turbine to obtain rotational power.
  • the present invention relates to a sealing device, a gas turbine, and an aeronautical engine for preventing high temperature gas from entering the turbine body through the gap.
  • General gas turbine is composed of a compressor, a combustor, and a turbine.
  • the compressor compresses the air taken in from the air intake port into high-temperature and high-pressure compressed air.
  • the combustor obtains high-temperature and high-pressure combustion gas by supplying fuel to the compressed air and burning it.
  • the turbine is driven by this combustion gas, and drives a generator connected on the same axis.
  • the high-temperature and high-pressure combustion gas generated in the combustor passes through a plurality of stationary blades and moving blades in the combustion gas passage, and the rotor rotates.
  • a sealing device called a rim seal. This rim seal supplies purge air to the disk cavity formed in the gap between the moving blade and the stationary blade, and ejects the purge air from the disk cavity toward the gap between the moving blade and the stationary blade, so that the intrusion of combustion gas Is to prevent.
  • Patent Document 1 An example of such a rim seal is described in Patent Document 1 below.
  • a plurality of stationary blades and moving blades are arranged at predetermined intervals in the circumferential direction, and a non-uniform pressure distribution is formed in the circumferential direction by the plurality of stationary blades and moving blades. Then, in the high pressure region, the combustion gas enters the turbine through the gap between the moving blade and the stationary blade, and in the low pressure region, the purge air in the disk cavity enters the combustion gas passage through the gap between the moving blade and the stationary blade. Therefore, as described in Patent Document 1 described above, even if multiple seals are arranged, it is difficult to sufficiently prevent the invasion of combustion gas from the gap between the moving blade and the stationary blade. On the other hand, in order to prevent the intrusion of combustion gas, it is conceivable to increase the purge air. However, this purge air is extracted from the compressor, and the gas turbine efficiency is lowered.
  • the present invention solves the above-described problems, and a gas turbine seal device and a gas turbine that improve gas turbine efficiency by suppressing the invasion of combustion gas into the turbine body with a small amount of purge air.
  • the purpose is to provide an aircraft engine.
  • a gas turbine seal device includes a seal portion provided between a platform of a turbine blade and an inner shroud of the turbine blade, the turbine blade, and the turbine blade. And an acoustic damper having a closed space communicating with the disk cavity through the opening.
  • the closed space portion is arranged on a radially inner side of the inner shroud.
  • the seal portion includes a first seal portion configured by disposing the platform with a predetermined gap inside in a radial direction from the inner shroud, and the opening. The portion is provided to face the first seal portion in the turbine axial direction.
  • the combustion gas entering the turbine from the gap between the platform and the inner shroud can be appropriately passed through the opening portion to the closed space portion.
  • the acoustic energy due to the pressure wave of the combustion gas can be appropriately attenuated in the closed space.
  • the seal portion includes a first seal portion configured by disposing the platform with a predetermined gap inside in a radial direction from the inner shroud, and the first seal. And a second seal portion provided radially inward of the portion, wherein the opening is provided on the radially outer side of the second seal portion.
  • the combustion gas entering the turbine through the gap between the platform and the inner shroud can reach the opening portion before reaching the second seal portion.
  • the acoustic energy generated by the pressure wave of the combustion gas can be appropriately attenuated in the closed space.
  • the seal portion includes a first seal portion configured by disposing the platform with a predetermined gap inside in a radial direction from the inner shroud, and the first seal.
  • a second seal portion provided radially inward of the portion, and the opening is provided between the first seal portion and the second seal portion in the radial direction.
  • the combustion gas entering the turbine from the gap between the platform and the inner shroud can be appropriately passed through the opening portion. Since it is introduced into the closed space, the acoustic energy due to the pressure wave of the combustion gas can be appropriately attenuated in the closed space.
  • the seal portion includes a first seal portion configured by disposing the platform with a predetermined gap inside in a radial direction from the inner shroud, and the first seal.
  • a second seal portion provided radially inward of the first portion, and the opening includes a first opening provided opposite to the first seal portion in a turbine axial direction, and the second seal portion. It has the 2nd opening part provided in the outer side of the radial direction of this.
  • the gap between the platform and the inner shroud is introduced into the turbine.
  • the invading combustion gas is appropriately introduced into the closed space through each opening, and the acoustic energy due to the pressure wave of the combustion gas can be appropriately attenuated in the closed space.
  • the closed space portion includes a first closed space portion positioned on the outer side in the radial direction and a second closed space portion positioned on the inner side in the radial direction.
  • An opening is provided in the first closed space, and the second opening is provided in the second closed space.
  • the pressure wave of the combustion gas introduced from each opening to the corresponding closed space can be appropriately attenuated.
  • the closed space portion is arranged on a radially inner side of the platform.
  • the closed space is provided on the platform on the movable side, the pressure wave of the combustion gas can be appropriately attenuated.
  • the seal portion is configured by extending a seal fin from the platform side with a predetermined gap inside in a radial direction from the inner shroud, and the radial direction from the seal fin.
  • the closed space is provided on the inside, and the opening is provided in the seal fin.
  • the closed space is provided by the front seal plate and the rear seal plate in the axial direction inside the platform in the radial direction, and the opening is provided in the rear seal plate. It is characterized by that.
  • the closed space is provided along the circumferential direction.
  • the pressure wave of the combustion gas can be appropriately attenuated in the circumferential direction of the moving blade and the stationary blade.
  • the closed space is divided into a plurality of portions in the circumferential direction by a partition plate.
  • the strength can be improved by providing a partition plate in the closed space.
  • the gas turbine of the present invention is a gas turbine having a compressor, a combustor, and a turbine, wherein the turbine is provided with a seal device for the gas turbine.
  • the combustion gas and its pressure wave are attenuated by the acoustic damper, so that the invasion of the combustion gas into the turbine body can be suppressed with a smaller amount of purge air than before, and the gas turbine efficiency can be improved. it can.
  • the aircraft engine of the present invention is an aircraft engine having a compressor, a combustor, and a turbine, wherein the turbine is provided with a gas turbine seal device.
  • the combustion gas and its pressure wave are attenuated by the acoustic damper, so that the invasion of the combustion gas into the turbine body can be suppressed with a smaller amount of purge air than before, and the gas turbine efficiency can be improved. it can.
  • the acoustic damper having the closed space communicating with the disk cavity between the turbine rotor blade and the turbine stationary blade through the opening is provided.
  • the combustion gas and its circumferential pressure distribution are attenuated by the acoustic damper, so that the invasion of the combustion gas into the turbine body can be suppressed with a smaller amount of purge air than before, and the gas turbine efficiency can be improved. Can do.
  • FIG. 1 is a sectional view showing the sealing device of the gas turbine of a 1st embodiment.
  • FIG. 2 is a schematic diagram illustrating the overall configuration of the gas turbine.
  • FIG. 3 is a cross-sectional view illustrating a gas turbine seal device according to a second embodiment.
  • FIG. 4 is a cross-sectional view illustrating a gas turbine seal device according to a third embodiment.
  • FIG. 5 is a cross-sectional view illustrating a gas turbine seal device according to a fourth embodiment.
  • FIG. 6 is a cross-sectional view illustrating a gas turbine seal device according to a fifth embodiment.
  • FIG. 7 is a cross-sectional view illustrating a gas turbine seal device according to a sixth embodiment.
  • FIG. 8 is a schematic view showing a space portion of the blade root portion on the platform side.
  • FIG. 9 is a schematic diagram showing the overall configuration of the aircraft engine.
  • FIG. 2 is a schematic diagram illustrating the overall configuration of the gas turbine according to the first embodiment.
  • the gas turbine of 1st Embodiment is comprised by the compressor 11, the combustor 12, and the turbine 13, as shown in FIG. This gas turbine is connected to a generator (not shown) on the same axis so that power can be generated.
  • the compressor 11 has an air intake 20 for taking in air, an inlet guide vane (IGV: Inlet Guide Vane) 22 is disposed in the compressor casing 21, and a plurality of stationary blades 23 and a plurality of moving blades. 24 are alternately arranged in the air flow direction (the axial direction of the rotor 32 to be described later), and a bleed chamber 25 is provided on the outside thereof.
  • the compressor 11 generates high-temperature and high-pressure compressed air by compressing the air taken in from the air intake port 20 and is supplied to the passenger compartment 14.
  • the combustor 12 is supplied with high-temperature and high-pressure compressed air and fuel that are compressed by the compressor 11 and stored in the vehicle compartment 14 and burns to generate combustion gas.
  • a plurality of stationary blades 27 and a plurality of moving blades 28 are alternately arranged in a turbine casing 26 in the flow direction of combustion gas (the axial direction of a rotor 32 described later).
  • the turbine casing 26 is provided with an exhaust chamber 30 on the downstream side via an exhaust casing 29, and the exhaust chamber 30 has an exhaust diffuser 31 connected to the turbine 13.
  • the turbine 13 is driven by the combustion gas from the combustor 12 and drives a generator connected on the same axis.
  • the compressor 11, the combustor 12, and the turbine 13 are provided with a rotor (rotary shaft) 32 so as to penetrate the central portion of the exhaust chamber 30.
  • the end of the rotor 32 on the compressor 11 side is rotatably supported by the bearing portion 33, and the end of the exhaust chamber 30 side is rotatably supported by the bearing portion 34.
  • the rotor 32 is fixed by a compressor 11 in which a plurality of disks on which the moving blades 24 are mounted are stacked.
  • a plurality of disks on which the moving blades 28 are mounted are stacked and fixed in the turbine 13, and a drive shaft of the generator is connected to an end portion on the exhaust chamber 30 side.
  • the compressor casing 21 of the compressor 11 is supported by the legs 35
  • the turbine casing 26 of the turbine 13 is supported by the legs 36
  • the exhaust chamber 30 is supported by the legs 37.
  • the air taken in from the air intake 20 by the compressor 11 passes through the inlet guide vane 22, the plurality of stationary vanes 23, and the moving vanes 24 and is compressed to become high-temperature and high-pressure compressed air. .
  • a predetermined fuel is supplied to the compressed air in the combustor 12 and burned.
  • high-temperature and high-pressure combustion gas generated in the combustor 12 passes through a plurality of stationary blades 27 and moving blades 28 in the turbine 13 to drive and rotate the rotor 32, and is connected to the rotor 32. Drive the generator.
  • the combustion gas is released into the atmosphere after the kinetic energy is converted into pressure by the exhaust diffuser 31 in the exhaust chamber 30 and decelerated.
  • Drawing 1 is a sectional view showing the sealing device of the gas turbine of a 1st embodiment.
  • the rotor 32 (see FIG. 2) is connected so that a plurality of turbine disks 41 can rotate integrally with a predetermined interval along the axial direction thereof.
  • a plurality of rotor blades 28 are fixed to the outer peripheral portion at a predetermined interval in the circumferential direction. That is, the turbine disk 41 has a disk shape, and a plurality of fitting grooves (not shown) along the axial direction are formed in the outer circumferential portion at equal intervals in the circumferential direction.
  • the blade 28 is integrally provided with a blade portion on the upper portion (outside) of the platform 42, and a blade root portion 43 that can be fitted in the fitting groove is integrally formed on the lower portion of the platform 42. Therefore, the rotor blade 28 is attached to the turbine disk 41 by slidingly fitting the blade root portion 43 into the fitting groove. Further, the space 44 between the blade root portions 43 adjacent in the circumferential direction is closed by a front seal plate (not shown) and a rear seal plate 45.
  • the stationary blade 27 is fixed to an inner shroud 46 whose base end portion has a ring shape, and a distal end portion is fixed to an outer shroud (not shown) having a ring shape.
  • the stationary blades 27 are arranged between the inner and outer shrouds 46, which are disposed between the rotor blades 28 in the axial direction and have a cylindrical shape, and are fixed at a predetermined interval in the circumferential direction.
  • the outer shroud is supported in the turbine casing 26 via a blade ring (not shown).
  • the inner shroud 46 has a seal ring retaining ring 47 fixed to the inner side.
  • the seal ring holding ring 47 is provided with a seal (not shown) so as to face the rim portion of the turbine disk 41 located inside thereof.
  • the sealing device 50 of the present embodiment includes a first seal portion 51 provided between the platform 42 of the moving blade (turbine moving blade) 28 and the inner shroud 46 of the stationary blade (turbine stationary blade) 27, An acoustic damper 55 having a closed space portion 54 communicating with the disk cavity 52 between the stator blades 27 via an opening 53 is provided.
  • the first seal part 51 and the closed space part 54 are continuous in the circumferential direction.
  • the sealing device 50 suppresses the high temperature gas (combustion gas) G from entering the disk cavity 52 formed between the moving blade 28 and the stationary blade 27.
  • the hot gas G flows in the axial direction through the gas passage in which the moving blade 28 and the stationary blade 27 are arranged, and a part of the hot gas g diverted from the hot gas G is entrained toward the disk cavity 52 to move the moving blade.
  • the sealing device 50 prevents the blade root 43 and the rotor 32 from entering the vicinity.
  • the moving blade 28 is provided with a first buffer cavity 61 on the downstream side in the flow direction of the hot gas G in the platform 42.
  • the first buffer cavity 61 is a recess formed to face the stationary blade rim 62 in the inner shroud 46 of the stationary blade 27 in the flow direction of the hot gas G.
  • the first buffer cavity 61 is provided between the downstream end 42a of the platform 42 facing the gas passage and the first seal fin 63 protruding from the platform 42 toward the disk cavity 52 on the inside in the radial direction. It has been. Therefore, the first buffer cavity 61 has a shape in which the flow of the high-temperature gas g is made uniform in the circumferential direction in the intrusion path where the high-temperature gas g branched from the flow of the high-temperature gas G reaches the disk cavity 52.
  • the first seal portion 51 narrows the cross-sectional area of the flow path to increase the flow path resistance of the hot gas g toward the inner side in the radial direction, that is, toward the disk cavity 52 side.
  • One seal fin 63 and a stationary blade rim 62 are included.
  • the first seal fin 63 extends from the radially inner side of the first buffer cavity 61 in the platform 42 to the downstream side in the flow direction of the high temperature gas G, and the tip portion is bent and protrudes radially outward.
  • the first seal fins 63 are disposed so as to overlap with the stationary blade rim 62 extending from the inner shroud 46 to the upstream side in the flow direction of the high temperature gas G with a predetermined gap in the radial direction.
  • the acoustic damper 55 is disposed inside the inner shroud 46 of the stationary blade 27 in the radial direction.
  • a seal ring holding ring 47 is fixed to the inner shroud 46 on the inner side, and a buffer plate 64 is disposed upstream of the inner shroud 46 and the seal ring holding ring 47 in the flow direction of the hot gas G.
  • the buffer plate 64 is supported by a coil spring 65 and a support shaft 66, and is in close contact with the seal ring holding ring 47 by an urging force, thereby forming an intra-blade channel 67.
  • the buffer plate 64 has a plate body 64a and a partition portion 64b having an L-shaped cross section.
  • the lower end of the plate body 64a is in close contact with the seal ring retaining ring 47, the upper end extends to the inner surface of the stationary blade rim 62 (inner shroud 46), and the tip is bent upstream in the flow direction of the hot gas G.
  • a fin 64c is provided. Therefore, the opening 53 is formed by arranging the inner surface of the stationary blade rim 62 and the outer surface of the fin 64c so as to overlap each other with a predetermined gap in the radial direction.
  • the buffer plate 64 has the closed space portion 54 formed by closely contacting the upper end portion of the partition portion 64b with the protruding portion 46a protruding inward from the inner surface of the inner shroud 46.
  • the closed space 54 communicates with the disk cavity 52 through the opening 53.
  • the opening 53 is provided so as to face the first seal portion 51 and the flow direction of the high temperature gas G (the turbine axis direction).
  • the closed space portion 54 includes an inner shroud 46 and a buffer plate 64, and is provided continuously along the circumferential direction. Note that the closed space portion 54 does not need to be provided continuously along the circumferential direction. For example, by providing the partition plate 68 with a predetermined interval in the circumferential direction of the closed space portion 54, the closed space portion 54 is surrounded. You may divide into multiple in a direction. Moreover, you may provide a some closed space part intermittently in the circumferential direction. Furthermore, the opening 53 may be continuous in the circumferential direction, or may be provided at a predetermined interval. In this case, the opening 53 may be provided at a position facing at least the first seal portion 51 in the axial direction (the flow direction of the hot gas G).
  • the acoustic damper 55 introduces the high temperature gas g and pressure wave from the opening 53 into the closed space 54 in the intrusion path where the high temperature gas g branched from the flow of the high temperature gas G reaches the disk cavity 52. To attenuate the pressure wave. Note that the length and gap amount of the opening 53 and the shape and volume of the closed space 54 are preset according to the wave number of the hot gas g circumferential pressure distribution.
  • the sealing device 50 configured as described above introduces compressed air into the disk cavity 52 as a sealing fluid through a blade flow path (not shown) formed in the stationary blade 27.
  • Cooling air (compressed air) C extracted from the compressor 11 is introduced into the blade flow passage 67 through the stationary blade 27 and ejected from the seal air supply hole 69.
  • This cooling air is used as the sealing air of the seal described above.
  • a part of the cooling air C is ejected from the seal air supply hole 69 and then flows into the disk cavity 52 through the gap of the seal 70 to become purge air. Therefore, the disk cavity 52 is held at a predetermined pressure and cooled by the introduction of the cooling air C.
  • the hot gas G flows through the gas passage in which the rotor blades 28 and the stationary blades 27 are arranged, and a part of the hot gas g is diverted toward the disk cavity 52.
  • the cooling air C is introduced into the blade flow passage 67 through the stationary blade 27 and ejected from the seal air supply hole 69, and then partially flows into the disk cavity 52 through the gap of the seal 70. . Therefore, the cooling air C is introduced into the disk cavity 52 so that the disk cavity 52 is maintained at a predetermined pressure, and the flow of the hot gas g to the disk cavity 52 is suppressed.
  • the hot gas g may enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27.
  • the sealing device 50 suppresses the high temperature gas g from entering the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27. That is, the high-temperature gas g which is going to enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27 first flows into the first buffer cavity 61 where it is agitated and mixed to thereby distribute the pressure in the circumferential direction. Is alleviated. Next, the hot gas g tends to enter the disk cavity 52 through the first seal portion 51. At this time, since the opening portion 53 of the acoustic damper 55 is opposed to the first seal portion 51, a part of the high temperature gas g that has passed through the first seal portion 51 passes through the opening portion 53 and is in the closed space portion 54. To be introduced.
  • the acoustic energy due to the pressure wave of the hot gas g is attenuated by resonating in the closed space 54.
  • the pressure distribution in the circumferential direction is further relaxed, and the intrusion amount of the hot gas g that passes through the first seal portion 51 and enters the disk cavity 52 is reduced.
  • the first seal portion 51 provided between the platform 42 of the moving blade 28 of the turbine 13 and the inner shroud 46 of the stationary blade 27, and the moving blade
  • An acoustic damper 55 having a closed space portion 54 communicating with the disk cavity 52 between the blade 28 and the stationary blade 27 via the opening 53 is provided.
  • the pressure wave is introduced into the closed space portion 54 through the opening 53 together with the combustion gas G. Then, the acoustic energy by the pressure wave is attenuated by resonating inside.
  • the circumferential pressure distribution of the first seal portion 51 is made uniform, and the gas turbine efficiency can be improved by suppressing the intrusion of the combustion gas G into the disk cavity 52 with a smaller amount of purge air than in the past. it can. That is, the amount of compressed air extracted from the compressor 11 can be reduced.
  • the closed space portion 54 is disposed on the inner side of the inner shroud 46 in the radial direction. Therefore, since the closed space portion 54 is provided in the inner shroud 46 on the stationary side, the structure can be simplified by effectively using the space portion.
  • the first seal portion 51 is provided by disposing the platform 42 with a predetermined gap inside the radial direction from the inner shroud 46, and the opening 53 is formed in the first seal portion 51. And facing the axial direction of the rotor 32. Accordingly, the combustion gas G that enters the disk cavity 52 through the gap between the platform 42 and the inner shroud 46 can be appropriately introduced into the closed space 54 through the opening 53, and the pressure wave of the combustion gas G Can be attenuated properly in the closed space 54.
  • the closed space portion 54 is provided along the circumferential direction. Therefore, the pressure wave of the combustion gas G can be appropriately attenuated in the region in the circumferential direction of the moving blade 28 and the stationary blade 27.
  • the closed space portion 54 is divided into a plurality of portions in the circumferential direction by a partition plate 68. Therefore, the strength of the buffer plate 64 can be improved by providing one or more partition plates in the closed space 54.
  • the seal device 50 is provided in the turbine 13. Therefore, the combustion gas G and its pressure wave are attenuated by the acoustic damper 55, so that the invasion of the combustion gas G into the turbine body can be suppressed with a smaller amount of purge air than before, and the gas turbine efficiency is improved. can do.
  • FIG. 3 is a cross-sectional view illustrating a gas turbine seal device according to a second embodiment.
  • symbol is attached
  • the sealing device 80 includes a first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • a second seal portion 71 provided on the inner side in the radial direction; and an acoustic damper 83 having a closed space portion 82 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening 81. ing.
  • the moving blade 28 is provided with a first buffer cavity 61 on the downstream side in the flow direction of the hot gas G in the platform 42.
  • the first buffer cavity 61 is a recess formed so as to face the stationary blade rim 62 in the inner shroud 46 of the stationary blade 27 in the flow direction of the high temperature gas G.
  • the first sealing fin 63 and the stationary blade rim 62 It is configured.
  • the moving blade 28 is provided with a second buffer cavity 72 on the inner peripheral side of the first seal fin 63.
  • the second buffer cavity 72 is a space surrounded by the inner peripheral surface of the first seal fin 63 and the outer peripheral surface of the second seal fin 73.
  • the second buffer cavity 72 is located downstream of the first buffer cavity 61 in the entry path through which the hot gas g reaches the disk cavity 52.
  • the acoustic damper 83 is disposed on the radially inner side of the inner shroud 46 of the stationary blade 27.
  • a seal ring retaining ring 47 is fixed to the inner shroud 46 on the inner side, and a buffer plate 84 is disposed upstream of the inner shroud 46 and the seal ring retaining ring 47 in the flow direction of the hot gas G.
  • the buffer plate 84 is supported by the coil spring 65 and the support shaft 66, and is in close contact with the seal ring holding ring 47 by an urging force, thereby forming the blade flow path 67.
  • the buffer plate 84 has a plate body 84a and a partition portion 84b having an L-shaped cross section.
  • the lower end of the plate body 84a is in close contact with the seal ring retaining ring 47, the upper end extends to the inner surface of the stationary blade rim 62 (inner shroud 46), and the tip is bent upstream in the flow direction of the hot gas G.
  • a fin 84c is provided. Therefore, the opening 81 is formed by arranging the inner surface of the stationary blade rim 62 and the outer surface of the fin 84c so as to overlap each other with a predetermined gap in the radial direction.
  • the buffer plate 84 has a closed space portion 82 formed by closely contacting the upper end portion of the partition portion 84b with the protruding portion 46a protruding inward from the inner surface of the inner shroud 46.
  • the closed space 82 communicates with the disk cavity 52 via the opening 81.
  • the opening 81 is provided so as to face the first seal portion 51 and the flow direction of the high temperature gas G (the turbine axis direction).
  • the closed space portion 82 is configured by the inner shroud 46 and the buffer plate 84, and is provided continuously along the circumferential direction.
  • the second seal portion 71 narrows the cross-sectional area of the flow path to increase the flow path resistance of the hot gas g toward the inner side in the radial direction, that is, toward the disk cavity 52 side. It is composed of two seal fins 73 and a buffer plate 84.
  • the second seal fin 73 extends from the radially inner side of the first seal fin 63 in the rear seal plate 45 to the downstream side in the flow direction of the high temperature gas G, and the tip is bent and protrudes outward in the radial direction. Yes.
  • the second seal fins 73 are arranged so as to overlap the fins 84c extending from the buffer plate 84 to the upstream side in the flow direction of the hot gas G with a predetermined gap in the radial direction.
  • the buffer plate 84 has a curved guide surface 84d that is recessed on the end surface of the fin 84c, and guides the hot gas g to the second seal fin 73 side. Therefore, the second buffer cavity 72 is a space surrounded by the inner peripheral surface of the first seal fin 63, the outer peripheral surface of the second seal fin 73, and the curved guide surface 84d of the buffer plate 84.
  • the opening 81 of the acoustic damper 83 is provided outside the second seal portion 71 in the radial direction.
  • the hot gas G is partly diverted and is wound toward the disk cavity 52.
  • the sealing device 80 suppresses the high temperature gas g from entering the disk cavity 52. That is, the high-temperature gas g which is going to enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27 first flows into the first buffer cavity 61 where it is agitated and mixed to thereby distribute the pressure in the circumferential direction. Is alleviated. Next, the hot gas g tends to enter the disk cavity 52 through the first seal portion 51.
  • the opening 81 of the acoustic damper 83 faces the first seal portion 51, a part of the high temperature gas g that has passed through the first seal portion 51 passes through the opening 81 and is a closed space portion 82.
  • the hot gas g and its pressure wave are introduced into the closed space portion 82, the acoustic energy due to the pressure wave of the hot gas g is attenuated by resonating in the closed space portion 82, and the pressure distribution in the circumferential direction is further increased. Alleviated.
  • the hot gas g that has not been introduced into the closed space 82 flows into the second buffer cavity 72, where it is stirred and mixed, thereby further reducing the circumferential pressure distribution.
  • the second seal portion 71 suppresses the intrusion of the high temperature gas g into the disk cavity 52.
  • the first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • a second seal portion 71 provided on the inner side in the radial direction, and an acoustic damper 83 having a closed space portion 82 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening portion 81 are provided.
  • the opening 81 is provided outside the second seal portion 71 in the radial direction.
  • the combustion gas G that enters the disk cavity 52 from the gap between the platform 42 and the inner shroud 46 is allowed to enter the second seal portion 71.
  • FIG. 4 is a cross-sectional view illustrating a gas turbine seal device according to a third embodiment.
  • symbol is attached
  • the sealing device 90 includes a first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • a second seal portion 71 provided on the inner side in the radial direction; and an acoustic damper 93 having a closed space portion 92 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening 91. ing.
  • the acoustic damper 93 is disposed on the inner side of the inner shroud 46 of the stationary blade 27 in the radial direction.
  • a seal ring retaining ring 47 is fixed to the inner shroud 46 on the inner side, and a buffer plate 94 is disposed upstream of the inner shroud 46 and the seal ring retaining ring 47 in the flow direction of the hot gas G.
  • the buffer plate 94 is supported by a coil spring 65 and a support shaft 66, and is in close contact with the seal ring holding ring 47 by an urging force, thereby forming an intra-blade channel 67.
  • the inner shroud 46 is provided with a protrusion 62 a that protrudes inward from the inner surface of the stationary blade rim 62.
  • the buffer plate 94 has a plate main body 94a and a partition portion 94b having an L-shaped cross section.
  • the plate body 94a has a lower end that is in close contact with the seal ring retaining ring 47, an upper end that extends to the inner surface of the protrusion 62a of the stationary blade rim 62, and a tip that is bent upstream in the flow direction of the hot gas G.
  • An extending fin 94c is provided. Therefore, the opening 91 is formed by arranging the inner surface of the protruding portion 62a of the stationary blade rim 62 and the outer surface of the fin 94c so as to overlap each other with a predetermined gap in the radial direction.
  • the buffer plate 94 has a closed space portion 92 formed by closely contacting the upper end portion of the partition portion 94b with the protruding portion 46a protruding inward from the inner surface of the inner shroud 46.
  • the closed space 92 communicates with the disk cavity 52 through the opening 91.
  • the opening 91 is provided between the first seal portion 51 and the second seal portion 71 in the radial direction.
  • the closed space portion 92 includes an inner shroud 46 and a buffer plate 94, and is provided continuously along the circumferential direction.
  • the hot gas G is partly diverted and is wound toward the disk cavity 52.
  • the sealing device 90 suppresses the intrusion of the high temperature gas g into the disk cavity 52. That is, the high-temperature gas g which is going to enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27 first flows into the first buffer cavity 61 where it is agitated and mixed to thereby distribute the pressure in the circumferential direction. Is alleviated. Next, the high-temperature gas g flows into the second buffer cavity 72 through the first seal portion 51 and is stirred and mixed here, whereby the circumferential pressure distribution is further relaxed. The hot gas g attempts to enter the disk cavity 52 through the second seal portion 71.
  • the opening 91 of the acoustic damper 93 is located on the outer side in the radial direction from the second seal portion 71, a part of the hot gas g that has passed through the first seal portion 51 passes through the opening 91. It is introduced into the closed space 92.
  • the high temperature gas g and its pressure wave are introduced into the closed space portion 92, the acoustic energy generated by the pressure wave of the high temperature gas g is attenuated by resonating in the closed space portion 92, and the pressure distribution in the circumferential direction is further increased. Alleviated.
  • the first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • a second seal portion 71 provided on the inner side in the radial direction, and an acoustic damper 93 having a closed space portion 92 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening 91 are provided.
  • the opening 91 is provided between the first seal portion 51 and the second seal portion 71 in the radial direction.
  • the combustion gas G that enters the disk cavity 52 from the gap between the platform 42 and the inner shroud 46 is appropriately introduced into the closed space 92 through the opening 91, and the acoustic energy due to the pressure wave of the combustion gas G can be appropriately attenuated in the closed space 92.
  • FIG. 5 is a cross-sectional view illustrating a gas turbine seal device according to a fourth embodiment.
  • symbol is attached
  • the sealing device 100 includes a first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • An acoustic damper having a second seal portion 71 provided on the inner side in the radial direction and a closed space portion 103, 104 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the openings 101, 102. 105.
  • the acoustic damper 105 is disposed on the inner side of the inner shroud 46 of the stationary blade 27 in the radial direction.
  • a seal ring retaining ring 47 is fixed to the inner shroud 46 on the inner side, and buffer plates 106 and 107 are disposed upstream of the inner shroud 46 and the seal ring retaining ring 47 in the flow direction of the hot gas G.
  • the buffer plate 107 is supported by the coil spring 65 and the support shaft 66, and is in close contact with the seal ring holding ring 47 by an urging force, thereby forming the blade flow path 67.
  • the buffer plate 106 is connected between the inner shroud 46 and the buffer plate 107.
  • the buffer plate 106 has a protrusion 106a and a plate body 106b.
  • the protruding portion 106a protrudes inward from the inner surface of the inner shroud 46, and the plate body 106b is provided with a fin 106c extending from the protruding portion 106a to the upstream side in the flow direction of the hot gas G and having a tip portion bent outward. ing. Therefore, the first opening 101 is formed by arranging the inner surface of the stationary blade rim 62 and the outer surface of the fin 106c so as to overlap each other with a predetermined gap in the radial direction.
  • the buffer plate 107 has a plate body 107a and a partition portion 107b having an L-shaped cross section.
  • the plate body 107a has a lower end portion that is in close contact with the seal ring holding ring 47, an upper end portion that extends to the inner surface of the buffer plate 106, and a tip portion that is bent and extends upstream in the flow direction of the hot gas G. Is provided. Therefore, the second opening 102 is formed by arranging the inner surface of the plate main body 106b of the buffer plate 106 and the outer surface of the fin 107c so as to overlap each other with a predetermined gap in the radial direction.
  • a first closed space 103 is formed by the inner shroud 46 and the buffer plate 106, and this closed space 103 communicates with the disk cavity 52 via the first opening 101.
  • the 1st opening part 101 is provided facing the 1st seal part 51 and the flow direction (turbine axial center direction) of the high temperature gas G.
  • a second closed space portion 104 is formed by the buffer plates 106 and 107, and this closed space portion 104 communicates with the disk cavity 52 via the second opening portion 102.
  • the second opening 102 is provided between the first seal portion 51 and the second seal portion 71 in the radial direction.
  • the hot gas G is partly diverted and is wound toward the disk cavity 52.
  • the sealing device 100 suppresses the high temperature gas g from entering the disk cavity 52. That is, the high-temperature gas g which is going to enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27 first flows into the first buffer cavity 61 where it is agitated and mixed to thereby distribute the pressure in the circumferential direction. Is alleviated.
  • the hot gas g tends to enter the disk cavity 52 through the first seal portion 51.
  • the first opening portion 101 of the acoustic damper 105 is opposed to the first seal portion 51, a part of the high temperature gas g that has passed through the first seal portion 51 passes through the first opening portion 101.
  • the hot gas g flows into the second buffer cavity 72 through the first seal portion 51, and is stirred and mixed here, whereby the circumferential pressure distribution is further relaxed.
  • the hot gas g attempts to enter the disk cavity 52 through the second seal portion 71.
  • the second opening portion 102 of the acoustic damper 105 is positioned on the outer side in the radial direction from the second seal portion 71, a part of the high temperature gas g that has passed through the first seal portion 51 is the first opening portion. 102 is introduced into the second closed space 104.
  • the first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • An acoustic damper having a second seal portion 71 provided on the inner side in the radial direction and a closed space portion 103, 104 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the openings 101, 102. 105.
  • the platform 42 and the inner shroud are provided. 46, the pressure distribution in the circumferential direction of the combustion gas G that enters the disk cavity 52 from the gap between them can be attenuated in two stages, and the combustion gas G to the disk cavity 52 with a smaller amount of purge air than in the prior art. Can be effectively suppressed.
  • the lengths and gap amounts of the openings 101 and 102 and the shapes and volumes of the closed spaces 103 and 104 are set in advance according to the wave number of the circumferential pressure distribution of the hot gas g.
  • the length and gap amount of the opening 101 and the shape and volume of the closed space 103 are set according to the wave number of the circumferential pressure distribution by the stationary blade 27, and the opening is opened according to the wave number of the circumferential pressure distribution by the moving blade 28.
  • FIG. 6 is a cross-sectional view illustrating a gas turbine seal device according to a fifth embodiment.
  • symbol is attached
  • the sealing device 110 includes a first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • a second seal portion 71 provided on the inner side in the radial direction; and an acoustic damper 113 having a closed space portion 112 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening 111. ing.
  • the acoustic damper 113 is disposed inside the platform 42 of the rotor blade 28 in the radial direction.
  • the blade 28 has a blade root 43 attached to the turbine disk 41, and a space 44 between the blade roots 43 adjacent in the circumferential direction is closed by a front seal plate and a rear seal plate 45.
  • the second seal fin 73 extends from the inside in the radial direction of the first seal fin 63 in the rear seal plate 45 to the downstream side in the flow direction of the hot gas G.
  • the second seal portion 71 is configured by the protruding portion 46 b of the stationary blade rim 62 and the second seal fin 73 in the flow direction of the high temperature gas g.
  • the buffer plate 114 has a bottom portion 114a and a wall portion 114b.
  • the bottom portion 114a is connected to the rear seal plate 45.
  • the wall portion 114b has a lower end portion connected to the bottom portion 114a and an upper end portion connected to the second seal fin. 73. Therefore, the closed space 112 is formed by the buffer plate 114, the rear seal plate 45, and the second seal fin 73.
  • the second seal fin 73 has an opening 111 that communicates the disk cavity 52 and the closed space 112.
  • a seal ring retaining ring 47 is fixed to the inner shroud 46 on the inner side, and a buffer plate 115 is disposed upstream of the inner shroud 46 and the seal ring retaining ring 47 in the flow direction of the high temperature gas G.
  • the buffer plate 115 is supported by a coil spring 65 and a support shaft 66, and is in close contact with the seal ring holding ring 47 by an urging force, thereby forming an intra-blade channel 67.
  • the hot gas G is partly diverted and is wound toward the disk cavity 52.
  • the sealing device 110 suppresses the intrusion of the high temperature gas g into the disk cavity 52. That is, the high-temperature gas g which is going to enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27 first flows into the first buffer cavity 61 where it is agitated and mixed to thereby distribute the pressure in the circumferential direction. Is alleviated. Next, the high-temperature gas g flows into the second buffer cavity 72 through the first seal portion 51 and is stirred and mixed here, whereby the circumferential pressure distribution is further relaxed. The hot gas g attempts to enter the disk cavity 52 through the second seal portion 71.
  • the opening 111 of the acoustic damper 113 is positioned on the moving blade 28 side, a part of the high temperature gas g that has passed through the first seal portion 51 is introduced into the closed space 112 through the opening 111. Is done.
  • the hot gas g and its pressure wave are introduced into the closed space portion 112
  • the acoustic energy due to the pressure wave of the hot gas g is attenuated by resonating in the closed space portion 112, and the pressure distribution in the circumferential direction is further increased. Alleviated.
  • the first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first seal portion 51.
  • a second seal portion 71 provided on the inner side in the radial direction, and an acoustic damper 113 having a closed space portion 112 communicating with the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening 111 are provided.
  • the acoustic damper 113 is disposed inside the platform 42 in the radial direction.
  • the combustion gas G entering the disk cavity 52 from the gap between the platform 42 and the inner shroud 46. Is appropriately introduced into the closed space 112 through the opening 111, and the acoustic energy generated by the pressure wave of the combustion gas G can be appropriately attenuated in the closed space 112. In this case, since the closed space 112 is provided on the platform 42 on the movable side, the pressure wave of the combustion gas G can be appropriately attenuated.
  • the second seal portion 71 is spaced apart from the inner shroud 46 in the radial direction by a predetermined gap, and the rear seal plate 45 and the rear seal plate 45 on the platform 42 side.
  • the second seal fin 73 is extended from the inside, the closed space portion 112 is provided on the inner side in the radial direction from the seal fin 73, and the opening 111 is provided in the second seal fin 73. Therefore, by providing the opening 111 and the closed space 112 using the second seal fin 73, the complexity of the structure can be suppressed.
  • FIG. 7 is a cross-sectional view illustrating a gas turbine sealing device according to a sixth embodiment
  • FIG. 8 is a schematic view illustrating a space portion of a blade root portion on the platform side.
  • symbol is attached
  • the sealing device 120 includes a first seal portion 51 provided between the platform 42 of the moving blade 28 and the inner shroud 46 of the stationary blade 27, and the first sealing portion 51.
  • a space portion (closed space portion) 44 communicating with the second seal portion 71 provided radially inside from the seal portion 51 and the disk cavity 52 between the moving blade 28 and the stationary blade 27 via the opening 121 is provided.
  • an acoustic damper 122 having the same.
  • the acoustic damper 122 is disposed inside the platform 42 of the rotor blade 28 in the radial direction.
  • the blade 28 has a blade root 43 attached to the turbine disk 41, and a space 44 between the blade roots 43 adjacent in the circumferential direction is closed by a front seal plate and a rear seal plate 45.
  • the second seal fin 73 extends from the inside in the radial direction of the first seal fin 63 in the rear seal plate 45 to the downstream side in the flow direction of the hot gas G.
  • the second seal portion 71 is configured by the protruding portion 46 b of the stationary blade rim 62 and the second seal fin 73 in the flow direction of the high temperature gas g.
  • the space portion 44 functions as a closed space portion of the present invention.
  • the rear seal plate 45 has an opening 121 formed radially outward from the second seal fin 73 so as to communicate the disk cavity 52 and the space 44.
  • the hot gas G is partly diverted and is wound toward the disk cavity 52.
  • the sealing device 120 suppresses the intrusion of the high temperature gas g into the disk cavity 52. That is, the high-temperature gas g which is going to enter the disk cavity 52 through the gap between the moving blade 28 and the stationary blade 27 first flows into the first buffer cavity 61 where it is agitated and mixed to thereby distribute the pressure in the circumferential direction. Is alleviated. Next, the high-temperature gas g flows into the second buffer cavity 72 through the first seal portion 51 and is stirred and mixed here, whereby the circumferential pressure distribution is relaxed. The hot gas g attempts to enter the disk cavity 52 through the second seal portion 71.
  • the opening 121 of the acoustic damper 122 is located on the moving blade 28 side, a part of the high temperature gas g that has passed through the first seal portion 51 is introduced into the space 44 through the opening 121.
  • the hot gas g and its pressure wave are introduced into the space 44, the acoustic energy generated by the pressure wave of the hot gas g is attenuated by resonating in the space 44, and the circumferential pressure distribution is further relaxed.
  • the space portion 44 is provided by the front seal plate and the rear seal plate 45 in the axial direction inside the platform 42 in the radial direction, and the opening 121 is formed in the rear portion.
  • the seal plate 45 is provided. Therefore, by configuring the acoustic damper 122 using the existing space 44, it is possible to suppress the complexity of the structure and the cost increase.
  • FIG. 9 is a schematic diagram showing the overall configuration of the aircraft engine.
  • the aircraft engine 200 is a gas turbine, and includes a fan casing 211 and a main body casing 212.
  • the fan 213 is accommodated in the fan casing 211, and the main body casing.
  • a compressor 214, a combustor 215, and a turbine 216 are accommodated in 212.
  • the fan 213 is configured by mounting a plurality of fan blades 222 on the outer peripheral portion of the rotating shaft 221.
  • the compressor 214 includes a low pressure compressor 223 and a high pressure compressor 224.
  • the combustors 215 are arranged downstream of the compressor 214 in the longitudinal direction of the compressed air, and a plurality of combustors 215 are arranged in the circumferential direction.
  • the turbine 216 is disposed downstream of the combustor 215 in the flow direction of the combustion gas, and includes a high pressure turbine 225 and a low pressure turbine 226.
  • the rotating shaft 221 of the fan 213 and the low-pressure compressor 223 are connected, and the low-pressure compressor 223 and the low-pressure turbine 226 are connected by the first rotor shaft 227.
  • the high-pressure compressor 224 and the high-pressure turbine 225 are connected by a second rotor shaft 228 having a cylindrical shape located on the outer peripheral side of the first rotor shaft 227.
  • the compressor 214 generates high-temperature and high-pressure compressed air by passing the air taken in from the air intake port through a plurality of stationary blades and moving blades (not shown) in the low-pressure compressor 223 and the high-pressure compressor 224.
  • the combustor 215 burns by supplying a predetermined fuel to the compressed air, and generates high-temperature and high-pressure combustion gas.
  • the turbine 216 is driven to rotate as the combustion gas generated by the combustor 215 passes through a plurality of stationary blades and moving blades (not shown) in the high-pressure turbine 225 and the low-pressure turbine 226.
  • the rotational force of the low-pressure turbine 226 is transmitted to the low-pressure compressor 223 by the first rotor shaft 227 for driving. Further, the rotational force of the high-pressure turbine 225 is transmitted to the high-pressure compressor 224 by the second rotor shaft 228 for driving. As a result, the fan 213 can be driven and thrust can be obtained from the exhaust gas discharged from the turbine 216.
  • An acoustic damper 55 having a closed space portion is provided. Therefore, even in the aircraft engine 200, the gas turbine efficiency can be improved by making it possible to suppress the intrusion of the combustion gas into the turbine body with a small amount of purge air.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un dispositif d'étanchéité pour une turbine à gaz, une turbine à gaz, et un moteur d'aéronef, ledit dispositif d'étanchéité comprenant une première section d'étanchéité (51), qui est située entre une plate-forme (42) d'une pale de rotor (28) d'une turbine (13) et un carénage intérieur (46) d'une aube de stator (27), et un amortisseur de bruit (55), qui a une section d'espace fermé (54) communiquant par l'intermédiaire d'une ouverture (53) avec une cavité de disque (52) entre la pale de rotor (28) et l'aube de stator (27). Ainsi, l'efficacité de la turbine à gaz est améliorée en permettant à l'infiltration de gaz de combustion dans le corps principal de turbine d'être empêchée à l'aide d'une petite quantité d'air de purge.
PCT/JP2015/085882 2015-03-06 2015-12-22 Dispositif d'étanchéité pour turbine à gaz, turbine à gaz et moteur d'aéronef WO2016143230A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2017504581A JP6383088B2 (ja) 2015-03-06 2015-12-22 ガスタービンのシール装置及びガスタービン、航空用エンジン
US15/554,572 US10641118B2 (en) 2015-03-06 2015-12-22 Sealing apparatus for gas turbine, gas turbine, and aircraft engine
DE112015006259.9T DE112015006259T5 (de) 2015-03-06 2015-12-22 Dichtungsvorrichtung für gasturbine, gasturbine und luftfahrzeug-antriebsmaschine
CN201580077457.5A CN107407158B (zh) 2015-03-06 2015-12-22 燃气轮机的密封装置以及燃气轮机、航空用发动机

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JP2015044952 2015-03-06
JP2015-044952 2015-03-06

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WO2016143230A1 true WO2016143230A1 (fr) 2016-09-15

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PCT/JP2015/085882 WO2016143230A1 (fr) 2015-03-06 2015-12-22 Dispositif d'étanchéité pour turbine à gaz, turbine à gaz et moteur d'aéronef

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US (1) US10641118B2 (fr)
JP (1) JP6383088B2 (fr)
CN (1) CN107407158B (fr)
DE (1) DE112015006259T5 (fr)
WO (1) WO2016143230A1 (fr)

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CN112483193A (zh) * 2020-11-27 2021-03-12 北京化工大学 一种可抑制亥姆霍兹共振燃气入侵的涡轮阻尼盘缘结构
US11459903B1 (en) 2021-06-10 2022-10-04 Solar Turbines Incorporated Redirecting stator flow discourager
KR20230119491A (ko) * 2022-02-07 2023-08-16 두산에너빌리티 주식회사 베인 팁 간극을 최소화할 수 있는 압축기 및 이를 포함하는 가스터빈

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US4218189A (en) * 1977-08-09 1980-08-19 Rolls-Royce Limited Sealing means for bladed rotor for a gas turbine engine
JPH10252412A (ja) * 1997-03-12 1998-09-22 Mitsubishi Heavy Ind Ltd ガスタービンシール装置
JPH10266807A (ja) * 1997-03-27 1998-10-06 Mitsubishi Heavy Ind Ltd ガスタービンシール装置

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JPH07301103A (ja) * 1994-05-06 1995-11-14 Ishikawajima Harima Heavy Ind Co Ltd ラビリンスシール通過空気のスワール促進装置
WO1998058158A1 (fr) * 1997-06-19 1998-12-23 Mitsubishi Heavy Industries, Ltd. Dispositif d'etancheite pour aubes de stator de turbine a gaz
EP0972910B1 (fr) 1998-07-14 2003-06-11 ALSTOM (Switzerland) Ltd Système d'étanchéité sans contact pour turbines à gaz
JP2010077868A (ja) * 2008-09-25 2010-04-08 Mitsubishi Heavy Ind Ltd ガスタービンのリムシール構造
JP5291790B2 (ja) * 2009-02-27 2013-09-18 三菱重工業株式会社 燃焼器およびこれを備えたガスタービン
JP2013181577A (ja) * 2012-02-29 2013-09-12 Mitsubishi Heavy Ind Ltd シール装置、及びこれを備えている回転機械
US8939711B2 (en) * 2013-02-15 2015-01-27 Siemens Aktiengesellschaft Outer rim seal assembly in a turbine engine
EP2959148B1 (fr) * 2013-02-20 2019-05-22 Rolls-Royce North American Technologies, Inc. Turbine à gaz dotée d'un passage de dérivation configurable
EP3009613B1 (fr) * 2014-08-19 2019-01-30 United Technologies Corporation Joints sans contact pour moteurs à turbine à gaz

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Publication number Priority date Publication date Assignee Title
US4218189A (en) * 1977-08-09 1980-08-19 Rolls-Royce Limited Sealing means for bladed rotor for a gas turbine engine
JPH10252412A (ja) * 1997-03-12 1998-09-22 Mitsubishi Heavy Ind Ltd ガスタービンシール装置
JPH10266807A (ja) * 1997-03-27 1998-10-06 Mitsubishi Heavy Ind Ltd ガスタービンシール装置

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DE112015006259T5 (de) 2017-11-30
JP6383088B2 (ja) 2018-08-29
JPWO2016143230A1 (ja) 2017-11-02
CN107407158A (zh) 2017-11-28
CN107407158B (zh) 2020-06-02
US20180073378A1 (en) 2018-03-15
US10641118B2 (en) 2020-05-05

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